Separating device and turbomachine comprising separating device

ABSTRACT

The invention relates to a separating device for a turbomachine, comprising at least one housing ( 12 ) that has at least one bearing receiving area ( 24 ), which defines at least one bearing axis ( 26 ), and at least one wheel-side area ( 28 ). The separating device also comprises at least one swirling unit ( 32 ), which is arranged on the housing ( 12 ) in particular, for deflecting and/or swirling at least one fluid and/or particle flow ( 34 ), wherein the swirling unit ( 32 ) has at least one flow recess ( 38 ) which is delimited by a wall ( 36 ) of the housing ( 12 ) and which extends within the wheel-side area ( 28 ) at a distance from the bearing axis ( 26 ). According to the invention, the swirling unit ( 32 ) comprises at least one seal gap element ( 40 ) which is arranged on a wall ( 36 ) of the housing ( 12 ) and which is designed to deflect and/or swirl at least one fluid and/or particle flow ( 34 ) flowing through the flow recess ( 38 ) along the bearing axis ( 26 ) and/or towards the bearing axis ( 26 ).

BACKGROUND OF THE INVENTION

A separating device for a turbomachine, having at least one housing which has at least one bearing receptacle defining at least one bearing axis and which has at least one impeller side chamber, and having at least one swirling unit, arranged in particular on the housing, for diverting and/or swirling at least one fluid and/or particle flow, wherein the swirling unit has at least one flow recess, which is delimited by a wall of the housing and which extends within the impeller side chamber so as to be spaced apart from the bearing axis, has already been proposed.

SUMMARY OF THE INVENTION

The invention proceeds from such a separating device for a turbomachine.

It is proposed that the swirling unit comprises at least one sealing gap element which is arranged on a wall of the housing and which is provided for diverting and/or swirling at least one fluid and/or particle flow flowing through the flow recess along the bearing axis and/or toward the bearing axis.

The sealing gap element is preferably configured as a molded part, as a sealing ring, as a sealing collar or the like. The sealing gap element is preferably fastened to the housing, in particular formed as a single piece with the housing. The term “as a single piece” is to be understood in particular to mean cohesively connected, for example by way of a welding process and/or adhesive bonding process etc., and particularly advantageously integrally molded, for example by production from one casting and/or by production in a single-component or multi-component injection molding process. The sealing gap element is particularly preferably of circular-ring-shaped configuration as viewed along the bearing axis. The sealing gap element is preferably of hollow cylindrical configuration. The sealing gap element preferably has an at least approximately rectangular cross-sectional area in a plane in which the bearing axis is arranged. The sealing gap element is preferably arranged uniformly around the bearing axis. The sealing gap element preferably has a central axis, wherein the sealing gap element is in particular configured so as to be symmetrical around the central axis. In particular, the sealing gap element is arranged such that the central axis of the sealing gap element is arranged within the bearing axis. The sealing gap element preferably has a maximum width of in particular at most 5 mm, preferably at most 3 mm and particularly preferably at most 2 mm. The maximum width of the sealing gap element is preferably oriented at least substantially perpendicular to the bearing axis and/or with respect to the central axis. The term “substantially perpendicular” is to be understood in particular to mean an orientation of a straight line or of a plane, in particular of a viewing plane, relative to a further straight line or a further plane, in particular the bearing axis, wherein the straight line or the plane and the further straight line or the further plane, in particular as viewed in a projection plane, enclose an angle of 90°, and the angle has a maximum deviation of in particular less than 8°, advantageously less than 5° and particularly advantageously less than 2°. Preferably, the maximum width of the sealing gap element is in particular at least 1 mm, preferably at least 1.5 mm and particularly preferably at least 2 mm. The sealing gap element preferably has at least one inner surface and at least one outer surface which are, in particular at least partially, arranged at least substantially parallel to one another. The statement that a surface, in particular the outer surface of the sealing gap element, is oriented “substantially parallel” to an axis, a plane or a further surface, in particular the inner surface of the sealing gap element, is to be understood in particular to mean that the surface has, at every point of the surface, a minimum spacing to the axis, to the plane or to the further surface which, for all points, deviates by less than 5%, preferably less than 3% and particularly preferably less than 1% from an average value of the minimum spacing of all points. The inner surface and the outer surface of the sealing gap element are preferably, in particular at least partially, arranged at least substantially parallel to the bearing axis. In particular, the outer surface of the sealing gap element is arranged at least predominantly on a side of the sealing gap element which is averted from the bearing axis. The inner surface of the sealing gap element is preferably arranged at least predominantly on a side of the sealing gap element which faces toward the bearing axis. The sealing gap element preferably has at least one sealing gap surface which is in particular arranged at least substantially perpendicular to the bearing axis. The sealing gap surface preferably extends, as viewed at least substantially perpendicularly with respect to the bearing axis, at least substantially over the entire maximum width of the sealing gap element. The sealing gap surface is particularly preferably configured as a circular ring. In particular, the sealing gap surface is delimited by the inner surface and/or the outer surface of the sealing gap element.

The separating device is preferably provided for preventing the fluid and/or particle flow from flowing from the impeller side chamber in the direction of the bearing axis. In particular, the fluid and/or particle flow is implemented within a fluid that is to be moved by means of the turbomachine. For example, the fluid and/or particle flow takes the form of contamination and/or residues within the fluid that is to be moved. The swirling unit is preferably provided for diverting the fluid and/or particle flow flowing through the flow recess along the bearing axis, and/or toward the bearing axis, into a direction which points away from the wall of the housing and/or which is oriented at least substantially parallel to the bearing axis and/or to a longitudinal extent of the sealing gap element.

The housing, in particular that wall of the housing which delimits the flow recess, is preferably configured such that the flow recess is of streamlined configuration as viewed at least substantially perpendicularly with respect to the bearing axis. In particular, that wall of the housing which delimits the flow recess has, as viewed at least substantially perpendicularly with respect to the bearing axis, a contour which is of rounded, in particular at least partially elliptical, configuration. In particular, the contour of that wall of the housing which delimits the flow recess is configured without corners. The flow recess is preferably arranged in an edge region of the impeller side chamber which is spaced apart from the bearing axis. In particular, the flow recess is fluidically connected to the impeller side chamber. The flow recess preferably extends at least substantially all the way around the bearing axis. In particular, the flow recess has, as viewed along a circumferential direction around the bearing axis, a cross-sectional area which, along the circumferential direction, has a maximum deviation of at most 5%, preferably at most 3% and particularly preferably at most 1%, of an average value of the cross-sectional area of the flow recess. The bearing receptacle is preferably arranged around the bearing axis. The impeller side chamber is preferably arranged around the bearing axis and/or the bearing receptacle. The housing preferably has a spiral chamber which is fluidically connected to the impeller side chamber and to the flow recess. The spiral chamber preferably extends at least substantially all the way around the bearing axis. The spiral chamber is preferably at least partially of helical configuration as viewed along the bearing axis. The spiral chamber particularly preferably adjoins the edge region of the impeller side chamber and/or adjoins the flow recess. The spiral chamber preferably comprises at least one outlet opening for a discharge of the fluid that is to be moved. In particular, the spiral chamber and the impeller side chamber are connected to one another via at least one fluid opening. The fluid opening preferably has, as viewed at least substantially perpendicularly with respect to the bearing axis, an opening width that is oriented at least substantially parallel to the bearing axis. The term “substantially parallel” is to be understood in particular to mean an orientation of a straight line or of a plane, in particular of the opening width of the fluid opening, relative to a further straight line or a further plane, in particular of the bearing axis, wherein the straight line or the plane has a deviation of in particular less than 8°, advantageously less than 5° and particularly advantageously less than 2°, relative to the further straight line or the further plane, in particular in a projection plane. The fluid opening preferably extends at least substantially all the way around the bearing axis. In particular, at at least one point in a section plane through the bearing axis, in particular over at least a predominant part of an extent along the circumferential direction, the opening width of the fluid opening is smaller than a maximum longitudinal extent of the spiral chamber at the point.

By means of the design according to the invention of the separating device, an undesired ingress of fluid and/or particle flows into the bearing receptacle can advantageously be prevented. An advantageously high separation rate of the fluid and/or particle flows can be achieved. An advantageously high degree of swirling of the fluid and/or particle flows in the impeller side chamber can be made possible.

It is furthermore proposed that the sealing gap element at least partially delimits the flow recess. The sealing gap element is preferably arranged on that wall of the housing which delimits the flow recess. In particular, as viewed at least substantially perpendicularly with respect to the bearing axis, the outer surface of the sealing gap element is formed in a connecting region of the sealing gap element and that wall of the housing which delimits the flow recess and, preferably flush, in a plane with that wall of the housing which delimits the flow recess. The outer surface of the sealing gap element is preferably rounded, in particular oriented transversely with respect to the bearing axis, in the connecting region of the sealing gap element and that wall of the housing which delimits the flow recess. An advantageously large flow recess can be realized, in particular because the flow recess can be formed across the sealing gap element into the impeller side chamber. An advantageously high degree of swirling of the fluid and/or particle flows in the flow recess can be made possible.

It is furthermore proposed that the swirling unit comprises at least one further sealing gap element which is arranged on a wall of the housing and which at least partially delimits the flow recess. The further sealing gap element is preferably configured as a molded part. The further sealing gap element is preferably fastened to the housing, in particular formed as a single piece with the housing. The further sealing gap element is particularly preferably of circular-ring-shaped configuration as viewed along the bearing axis. The further sealing gap element is preferably of at least partially hollow cylindrical configuration. The further sealing gap element preferably has a central axis. In particular, the further sealing gap element is arranged such that the central axis of the further sealing gap element is arranged within the bearing axis. The further sealing gap element preferably has a maximum width of in particular at most 5 mm, preferably at most 3 mm and particularly preferably at most 2 mm. In particular, the maximum width of the further sealing gap element is oriented at least substantially perpendicular to the bearing axis and/or to the central axis of the further sealing gap element. Preferably, the maximum width of the further sealing gap element is in particular at least 1 mm, preferably at least 1.5 mm and particularly preferably at least 2 mm. The further sealing gap element preferably has at least one inner surface and at least one outer surface which are at least partially arranged at least substantially parallel to one another. The inner surface and the outer surface of the further sealing gap element are preferably at least partially arranged at least substantially parallel to the bearing axis. The further sealing gap element preferably has at least one side surface which is arranged in particular transversely, preferably at least partially at least substantially perpendicularly, with respect to the bearing axis. In particular, the side surface of the further sealing gap element is delimited by the inner surface and/or the outer surface of the further sealing gap element. The further sealing gap element is preferably arranged on that wall of the housing which delimits the flow recess. In particular, the outer surface of the further sealing gap element is arranged at least predominantly on a side of the further sealing gap element which is averted from the bearing axis. The inner surface of the further sealing gap element is preferably arranged at least predominantly on a side of the further sealing gap element which faces toward the bearing axis. In particular, as viewed at least substantially perpendicularly with respect to the bearing axis, the inner surface of the further sealing gap element is formed in a connecting region of the further sealing gap element and that wall of the housing which delimits the flow recess and, preferably flush, in a plane with that wall of the housing which delimits the flow recess. The inner surface of the sealing gap element is preferably rounded, in particular oriented transversely with respect to the bearing axis, in the connecting region of the further sealing gap element and that wall of the housing which delimits the flow recess. The further sealing gap element is particularly preferably configured and/or arranged such that the further sealing gap element, in particular the outer surface of the further sealing gap element, at least partially delimits the spiral chamber. In particular, the further sealing gap element is arranged between the impeller side chamber and the spiral chamber. The further sealing gap element, in particular the side surface of the further sealing gap element, preferably at least partially delimits the fluid opening. In particular, the further sealing gap element has a greater maximum transverse extent than the sealing gap element, in particular at least substantially parallel to the bearing axis. An advantageously directed flow into the flow recess can be made possible, in particular because a fluid and/or particle flow can be conducted along the further sealing gap element directly into the flow recess. An advantageously large flow recess can be made possible, in particular because the flow recess can be formed as far as a side surface of the further sealing gap element.

It is furthermore proposed that the swirling unit comprises at least one, in particular the abovementioned, further sealing gap element which, as viewed at least substantially perpendicularly with respect to the bearing axis, has a minimum radial spacing to the bearing axis which is greater than a minimum radial spacing of the sealing gap element and of the bearing axis, wherein the flow recess is, as viewed from the bearing axis, arranged between the sealing gap element and the further sealing gap element. The minimum radial spacings of the sealing gap element and of the further sealing gap element to the bearing axis preferably extend at least substantially perpendicular to the bearing axis. The minimum radial spacing of the sealing gap element preferably extends from the inner surface of the sealing gap element to the bearing axis. The minimum radial spacing of the further sealing gap element is preferably arranged from the inner surface of the further sealing gap element to the bearing axis. The minimum radial spacing of the sealing gap element is preferably at least 40%, preferably at least 50% and particularly preferably at least 60% of the minimum radial spacing of the further sealing gap element. It is particularly preferable if the flow recess is spanned within the impeller side chamber by the sealing gap element and the further sealing gap element together with that wall of the housing which delimits the flow recess. An advantageous arrangement of the flow recess, in particular between the sealing gap elements, can be made possible. An advantageously large flow recess can be made possible, in particular because the flow recess can be spanned by the two sealing gap elements.

It is furthermore proposed that the swirling unit comprises at least one, in particular the abovementioned, further sealing gap element, wherein at least two outer surfaces of the further sealing gap element which adjoin one another and which form a sealing edge, in particular the abovementioned inner surface, outer surface and/or side surface, span at least an angle of less than 90°, preferably of less than 800 and particularly preferably of less than 70°, as viewed at least substantially perpendicularly with respect to the bearing axis, in particular in a vicinity of the sealing edge of the further sealing gap element. The side surface of the further sealing gap element and the outer surface or the inner surface of the further sealing gap element preferably span at least an angle that is in particular less than 90°, preferably less than 800 and particularly preferably less than 70°, in particular in a vicinity of the sealing edge of the further sealing gap element. A “vicinity” is to be understood in particular to mean a region around a component, in particular around the sealing edge, where every point within the region has a maximum spacing of at most 5 mm, preferably of at most 3 mm and particularly preferably of 1 mm, to the component. In particular, the sealing edge of the further sealing gap element is arranged at least substantially perpendicular to the bearing axis and at least substantially all the way around the bearing axis. An advantageously small fluid and/or particle flow from the spiral chamber, in particular past the further sealing gap element, in particular past the sealing edge of the further sealing gap element, into the impeller side chamber and the flow recess can be achieved. An undesired ingress of fluid and/or particle flows into the bearing receptacle can advantageously be prevented.

It is furthermore proposed that the swirling unit comprises at least one, in particular the abovementioned, further sealing gap element which has a sealing edge, in particular the abovementioned sealing edge or a further sealing edge which is arranged such that at least one of two outer surfaces, which form the sealing edge of the further sealing gap element, in particular the abovementioned inner surface, of the further sealing gap element, is oriented at least substantially parallel to the bearing axis. An advantageously small flow of a fluid and/or particle flow from the spiral chamber, in particular past the further sealing gap element, in particular past the sealing edge of the further sealing gap element, into the impeller side chamber and the flow recess can be achieved. An undesired ingress of fluid and/or particle flows into the bearing receptacle can advantageously be prevented.

Also proposed is a turbomachine, in particular a coolant pump, having at least one drive unit which has at least one drive axis, having at least one conveying unit, in particular an impeller disk, which is driven around the drive axis and which serves for conveying a fluid, in particular the abovementioned fluid, in particular a coolant, and which has at least one conveying element, in particular a vane, and having at least one separating device according to the invention, wherein the conveying unit is arranged at least predominantly within the impeller side chamber around the drive axis.

In particular, the drive axis is arranged within the bearing axis of the separating device. The conveying unit preferably has at least one drive shaft which is arranged on the drive axis. The conveying element preferably extends from the drive shaft into the impeller side chamber. The conveying element particularly preferably has, in particular at least substantially perpendicularly with respect to the drive axis, a maximum transverse extent that is smaller than a minimum radial spacing of the further sealing gap element, in particular of the inner surface of the further sealing gap element, and the drive shaft. The maximum transverse extent of the conveying element is preferably greater than a minimum radial spacing of the sealing gap element, in particular of the inner surface of the sealing gap element, and the drive shaft. The conveying element preferably delimits at least one conveying channel for conveying the fluid. The conveying channel preferably extends from a conveying inlet of the conveying channel, arranged at least substantially parallel to the drive axis, to a conveying outlet of the conveying channel, oriented at least substantially perpendicular to the drive axis. The conveying unit, in particular the conveying element, is preferably provided for directing a fluid and/or particle flow, which has been diverted and/or swirled by the flow recess and the sealing gap element, along a wall of the conveying unit, in particular of the conveying element, in a direction pointing away from the drive axis, preferably by way of a centrifugal force resulting from a rotation of the conveying element. It is conceivable for the conveying unit, in particular the conveying element, to comprise, on a side facing toward the flow recess, at least one fluid-directing element which is provided for directing a fluid and/or particle flow, which has been directed onto the wall, in a direction pointing away from the drive axis, in particular pointing toward the further sealing gap element. For example, the fluid-directing element is configured as a molded part, as a flow element, as a surface structure, as a fin and/or as some other fluid-directing element that appears expedient to a person skilled in the art. In particular, the conveying unit has a multiplicity of conveying elements which are in particular arranged uniformly around the drive axis and which delimit a multiplicity of conveying channels.

By means of the embodiment according to the invention of the turbomachine, an undesired ingress of fluid and/or particle flows into intermediate spaces of the drive shaft and of the bearing receptacle can advantageously be prevented. An advantageously high separation rate of the fluid and/or particle flows can be achieved. An advantageously high degree of swirling of the fluid and/or particle flows in the impeller side chamber can be made possible.

It is furthermore proposed that a maximum spacing, oriented at least substantially parallel to the drive axis, between the sealing gap element and the conveying element is less than 2 mm, preferably less than 1.5 mm and particularly preferably less than 1 mm. It is preferable if the maximum spacing, oriented at least substantially parallel to the drive axis, between the sealing gap element and the conveying element extends from the sealing gap surface of the sealing gap element to the conveying element, in particular to at least one surface of the conveying element which is oriented at least substantially perpendicular to the drive axis. The sealing gap element and/or the conveying element is preferably arranged such that a sealing gap is formed between the sealing gap element and the conveying element, in particular by the maximum spacing. A flow out of the flow recess between the sealing gap element and the conveying element can advantageously be prevented. A fluid and/or particle flow within the flow recess can advantageously be guided past the sealing gap formed between the sealing gap element and the conveying element.

It is furthermore proposed that the swirling unit has at least one, in particular the abovementioned, further sealing gap element which, as viewed at least substantially perpendicularly with respect to the drive axis, is arranged at least partially within a maximum longitudinal extent of the conveying element. In particular, the maximum longitudinal extent is oriented at least substantially parallel to the drive axis. The further sealing gap element is preferably arranged, as viewed at least substantially perpendicularly with respect to the drive axis, outside a maximum longitudinal extent of the conveying outlet of the conveying channel, which is in particular oriented at least substantially parallel to the drive axis. The maximum longitudinal extent of the conveying outlet of the conveying channel preferably corresponds at least substantially to the opening width of the fluid opening, which is in particular at least partially delimited by the further sealing gap element. In particular, the conveying element is arranged relative to the separating device such that the conveying outlet and the fluid opening are, as viewed in at least one section plane of the turbomachine through the drive axis, arranged congruently one behind the other proceeding from the drive axis. Preferably, as viewed in particular in at least one section plane of the turbomachine through the drive axis, the side surface of the further sealing gap element is arranged at least partially in a plane with an inner surface, which delimits the conveying outlet, of the conveying element. The inner surface, which delimits the conveying outlet, of the conveying element is preferably oriented at least substantially perpendicular to the drive axis. The inner surface, which delimits the conveying outlet, of the conveying element is arranged so as to be averted from the flow recess. An advantageously small fluid and/or particle flow out of the spiral chamber back into the flow recess can be achieved. A direct flow of a fluid and/or particle flow from the conveying channel into the flow recess can advantageously be prevented.

It is furthermore proposed that a maximum spacing, oriented at least substantially perpendicular to the drive axis, between the further sealing gap element and the conveying element is less than 2 mm, preferably less than 1.5 mm and particularly preferably less than 1 mm. The maximum spacing, oriented at least substantially perpendicularly with respect to the drive axis, between the further sealing gap element and the conveying element preferably extends from the inner surface of the further sealing gap element to a side surface of the conveying element that borders the conveying outlet, wherein, in particular, the side surface of the conveying element is at least partially oriented at least substantially parallel to the drive axis. The further sealing gap element and/or the conveying element is preferably arranged such that a further sealing gap is formed between the further sealing gap element and the conveying element, in particular by the maximum spacing. An advantageously small fluid and/or particle flow out of the spiral chamber back into the flow recess, in particular through the further sealing gap, can be achieved. A direct flow of a fluid and/or particle flow from the conveying channel into the flow recess can advantageously be prevented, in particular because the further sealing gap is arranged at least substantially parallel to an outflow direction of a fluid and/or particle flow out of the conveying outlet, wherein a fluid and/or particle flow flowing out of the conveying outlet is conducted past the sealing gap.

It is furthermore proposed that the conveying element has at least one bevel and/or at least one rounded portion in an edge region on at least a side facing toward the sealing gap element and/or the flow recess. The bevel and/or the rounded portion preferably extends at least partially along the circumferential direction around the drive axis. In particular in an embodiment in which the conveying element has the rounded portion, the rounded portion is preferably arranged on the side surface of the conveying element. In particular in an embodiment in which the conveying element has the bevel, the bevel is delimited by the side surface of the conveying element and/or by that surface of the conveying element which is oriented at least substantially perpendicular to the drive axis and which in particular forms the sealing gap. The conveying element particularly preferably has at least one sealing edge which is in particular delimited by the side surface and by the inner surface, which delimits the conveying outlet, of the conveying element. In particular, the sealing edge of the conveying element is at least partially configured so as to run at least substantially perpendicular to the drive axis and along the circumferential direction around the drive axis. The side surface and the inner surface, which delimits the conveying outlet, of the conveying element preferably at least partially, in particular in a vicinity around the sealing edge of the conveying element, span an angle of in particular at most 90°, preferably at most 800 and particularly preferably at most 70°. An advantageously large flow out of the flow recess into the spiral chamber can be achieved, in particular because a fluid and/or particle flow diverted and/or swirled by the flow recess and the sealing gap element can advantageously be conducted past the bevel and/or the rounded portion.

It is furthermore proposed that the sealing gap element has a minimum radial spacing to the drive axis which corresponds to at most 90%, in particular at most 80%, preferably at most 70% and particularly preferably at most 60%, of a maximum radial extent of the conveying element around the drive axis. Preferably, the minimum radial spacing of the sealing gap element to the drive axis corresponds in particular to at least 30%, preferably at least 40% and particularly preferably at least 50%, of the maximum radial extent of the conveying element around the drive axis. In particular, the minimum radial spacing of the sealing gap element to the drive axis extends at least substantially perpendicular to the drive axis. The minimum radial spacing of the sealing gap element to the drive axis preferably extends from the inner surface of the sealing gap element to the drive axis. An advantageously large flow recess can be achieved, in particular because the further sealing gap element that delimits the flow recess is arranged around the drive axis outside the maximum radial extent of the conveying element. An advantageously effective recirculation of a fluid and/or particle flow from the flow recess into the spiral chamber can be made possible, in particular because a high rotational speed of the conveying element in an outer edge region of the conveying element can give rise to an increased centrifugal force for the diversion of the fluid and/or particle flow.

It is not the intention here for the separating device according to the invention and/or the turbomachine according to the invention to be limited to the use and embodiment described above. In particular, the separating device according to the invention and/or the turbomachine according to the invention may, in order to perform a function described herein, have a number of individual elements, components and units that deviates from a number stated herein. Furthermore, where value ranges are stated in this disclosure, it is also the intention for values lying within the stated boundaries to be disclosed and usable as desired.

BRIEF DESCRIPTION OF THE DRAWINGS

Further advantages will emerge from the following description of the drawings. The drawings illustrate an exemplary embodiment of the invention. The drawings, the description and the claims contain numerous features in combination. A person skilled in the art will expediently also consider the features individually and combine them to form meaningful further combinations.

In the drawings:

FIG. 1 shows a schematic cross section of a turbomachine according to the invention, having a separating device according to the invention, through a central plane of the turbomachine,

FIG. 2 shows a schematic detailed view of the cross section of the turbomachine according to the invention in a region of an impeller side chamber of the separating device according to the invention,

FIG. 3 shows a schematic detailed view of the cross section of the turbomachine according to the invention in a region of the impeller side chamber of the separating device according to the invention, with fluid flows through a sealing gap of the turbomachine, and

FIG. 4 shows a schematic cross section of the turbomachine according to the invention, having the separating device according to the invention, through a plane oriented perpendicular to the central plane of the turbomachine, with exemplary fluid flows through the sealing gap of the turbomachine.

DETAILED DESCRIPTION

FIG. 1 shows a cross section through a turbomachine 10. The turbomachine 10 is configured as a coolant pump. Other embodiments of the turbomachine 10 are however also conceivable. The turbomachine 10 has a housing 12, a drive unit 14 with a drive axis 16, a conveying unit 18 which is driven around the drive axis 16 and which serves for conveying a fluid, in particular a coolant, and a separating device 20. The conveying unit 18 is configured as an impeller disk and comprises a multiplicity of conveying elements 22 configured as vanes, of which in particular only one conveying element 22 is shown in the figures. Other embodiments of the conveying unit 18 are however also conceivable. The housing 12 is configured as part of the separating device 20. The housing 12 has a bearing receptacle 24 that defines a bearing axis 26. The bearing receptacle 24 is preferably arranged around the bearing axis 26. The bearing axis 26 is configured within the drive axis 16. In particular, the cross section of the turbomachine 10 shown in FIG. 1 runs through the bearing axis 26 and the drive axis 16. The housing 12 has an impeller side chamber 28 which is arranged in particular between the conveying unit 18, in particular the conveying element 22, and the housing 12, in particular inner walls of the housing 12. The impeller side chamber 28 is preferably arranged around the bearing axis 26 and/or the bearing receptacle 24. The conveying unit 18 comprises a drive shaft 30 on which the conveying elements 22 are arranged. The drive unit 14 is provided for driving the conveying unit 18, via the drive shaft 30, around the drive axis 16, wherein, in particular, the conveying elements 22 are moved around the drive axis 16. The conveying elements 22 extend from the drive shaft 30 into the impeller side chamber 28. The drive shaft 30 and the drive unit 14 are arranged at least partially within the bearing receptacle 24 of the housing 12. The separating device 20 comprises a swirling unit 32 for diverting and/or swirling at least one fluid and/or particle flow 34. The swirling unit 32 is arranged on the housing 12. The swirling unit 32 comprises a flow recess 38 which is delimited by a wall 36 of the housing 12 and which extends within the impeller side chamber 28 so as to be spaced apart from the bearing axis 26. The swirling unit 32 comprises a sealing gap element 40 which is arranged on the wall 36 of the housing 12 and which is provided for diverting and/or swirling at least one fluid and/or particle flow 34 flowing through the flow recess 38 along the bearing axis 26 and/or toward the bearing axis 26.

The conveying elements 22 delimit in each case one conveying channel 42 for conveying the fluid. The conveying channel 42 extends within the conveying element 22 from a conveying inlet 44 of the conveying channel 42, arranged at least substantially parallel to the drive axis 16, to a conveying outlet 46 of the conveying channel 42, oriented at least substantially perpendicular to the drive axis 16. The conveying unit 18, in particular the conveying element 22, is preferably provided for directing a fluid and/or particle flow 34, which has been diverted and/or swirled by the flow recess 38 and the sealing gap element 40, along a wall 48 of the conveying unit 18, in particular of the conveying element 22, in the direction 50 pointing away from the drive axis 16, preferably by way of a centrifugal force resulting from a rotation of the conveying element 22 about the drive axis 16. It is conceivable for the conveying unit 18, in particular the conveying elements 22, to comprise, on a side facing toward the flow recess 38, at least one fluid-directing element 52 which is provided for directing a fluid and/or particle flow 34, which has been directed onto the wall 48 of the conveying unit 18, in a direction 50 pointing away from the drive axis 16. For example, the fluid-directing element 52 is configured as a molded part, as a flow element, as a surface structure, as a fin and/or as some other fluid-directing element 52 that appears expedient to a person skilled in the art for diverting a fluid and/or particle flow 34.

The sealing gap element 40 is configured as a molded part configured as a sealing collar. The sealing gap element 40 is formed as a single piece with the housing 12. The sealing gap element 40 is of circular-ring-shaped configuration as viewed along the bearing axis 26. The sealing gap element 40 is at least predominantly of hollow cylindrical configuration. The sealing gap element 40 has an at least approximately rectangular cross-sectional area 54 in a plane in which the bearing axis 26 is arranged. The sealing gap element 40 is arranged uniformly around the bearing axis 26, wherein, in particular, the cross-sectional area 54 of the sealing gap element 40 is configured to be at least substantially constant along a circumferential direction 56 around the bearing axis 26. The sealing gap element 40 has a central axis 58, wherein the sealing gap element 40 is in particular configured so as to be symmetrical around the central axis 58. The sealing gap element 40 is arranged such that the central axis 58 of the sealing gap element 40 is arranged within the bearing axis 26. The sealing gap element 40 has an inner surface 60 and an outer surface 62 which are in particular at least partially arranged at least substantially parallel to one another. Preferably, the inner surface 60 and the outer surface 62 of the sealing gap element 40 are in particular at least partially arranged at least substantially parallel to the bearing axis 26. The outer surface 62 of the sealing gap element 40 is arranged at least predominantly on a side of the sealing gap element 40 which is averted from the bearing axis 26. The inner surface 60 of the sealing gap element 40 is arranged at least predominantly on a side of the sealing gap element 40 which faces toward the bearing axis 26. The sealing gap element 40 has a sealing gap surface 64 which is in particular arranged at least substantially perpendicular to the bearing axis 26. The sealing gap surface 64 is particularly preferably configured as a circular ring. In particular, the sealing gap surface 64 is delimited by the inner surface 60 and/or the outer surface 62 of the sealing gap element 40. Other configurations of the sealing gap element 40 are however also conceivable, for example in the form of a sealing ring and/or with a shape that differs from a hollow cylinder, in particular with a different arrangement on the housing 12.

The housing 12, in particular that wall 36 of the housing 12 which delimits the flow recess 38, is configured such that the flow recess 38 is of streamlined configuration as viewed at least substantially perpendicularly with respect to the bearing axis 26. That wall 36 of the housing 12 which delimits the flow recess 38 has, as viewed at least substantially perpendicularly with respect to the bearing axis 26, a contour 66 which is of rounded, in particular at least partially elliptical, configuration. In particular, the contour 66 of that wall 36 of the housing 12 which delimits the flow recess 38 is configured without corners. The flow recess 38 is arranged in an edge region 68 of the impeller side chamber 28 which is spaced apart from the bearing axis 26. The flow recess 38 is fluidically connected to the impeller side chamber 28. The flow recess 38 extends at least substantially all the way around the bearing axis 26. The flow recess 38 has, as viewed along the circumferential direction 56 around the bearing axis 26, a cross-sectional area 70 which, along the circumferential direction 56, has a maximum deviation of at most 5%, preferably at most 3% and particularly preferably at most 1%, of an average value of the cross-sectional area 70 of the flow recess 38. The housing 12 has a spiral chamber 72 which is fluidically connected to the impeller side chamber 28 and to the flow recess 38. The spiral chamber 72 extends at least substantially all the way around the bearing axis 26. The spiral chamber 72 is at least partially of helical configuration as viewed along the bearing axis 26. The spiral chamber 72 adjoins the edge region 68 of the impeller side chamber 28 and/or adjoins the flow recess 38. The spiral chamber 72 comprises at least one outlet opening 74 for the discharge of the fluid that is to be moved (cf. FIG. 4 ). The spiral chamber 72 and the impeller side chamber 28 are connected to one another via a fluid opening 76. The fluid opening 76 has, as viewed at least substantially perpendicularly with respect to the bearing axis 26, an opening width 78 that is oriented at least substantially parallel to the bearing axis 26. The fluid opening 76 extends at least substantially all the way around the bearing axis 26. In particular, at at least one point in a section plane through the bearing axis 26, in particular over at least a predominant part of an extent along the circumferential direction 56, the opening width 78 of the fluid opening 76 is smaller than a maximum longitudinal extent 80 of the spiral chamber 72 at the point.

In particular, a fluid and/or particle flow 34 that is moved by means of the conveying unit 18 flows at least partially along the wall 36 of the housing 12 from the spiral chamber 72 into the impeller side chamber 28 and the flow recess 38 in the direction of the bearing axis 26. The fluid and/or particle flow 34 is shown in the figures with an exemplary course of the flow in each case. The separating device 20 is preferably provided for preventing the fluid and/or particle flow 34 from flowing from the impeller side chamber 28 in the direction of the bearing axis 26. In particular, the fluid and/or particle flow 34 is implemented within a fluid that is to be moved by means of the turbomachine 10. For example, the fluid and/or particle flow 34 takes the form of contamination and/or residues within the fluid that is to be moved. The swirling unit 32 is preferably provided for diverting the fluid and/or particle flow 34 flowing through the flow recess 38 along the bearing axis 26, and/or toward the bearing axis 26, into a direction 82 which points away from the wall 36 of the housing 12 and/or which is oriented at least substantially parallel to the bearing axis 26 and/or to a longitudinal extent of the sealing gap element 40.

The sealing gap element 40 at least partially delimits the flow recess 38. The sealing gap element 40 is arranged on that wall 36 of the housing 12 which delimits the flow recess 38. As viewed at least substantially perpendicularly with respect to the bearing axis 26, the outer surface 62 of the sealing gap element 40 is formed in a connecting region 86 of the sealing gap element 40 and that wall 36 of the housing 12 which delimits the flow recess 38 and, preferably flush, in a plane with that wall 36 of the housing 12 which delimits the flow recess 38. The outer surface 62 of the sealing gap element 40 is rounded, in particular oriented transversely with respect to the bearing axis 26, in the connecting region 86 of the sealing gap element 40 and that wall 36 of the housing 12 which delimits the flow recess 38.

The swirling unit 32 comprises a further sealing gap element 88 which is arranged on the wall 36 of the housing 12 and which at least partially delimits the flow recess 38. The further sealing gap element 88 is configured as a molded part. Other embodiments of the further sealing gap element 88 are however also conceivable. The further sealing gap element 88 is formed as a single piece with the housing 12. The further sealing gap element 88 is of circular-ring-shaped configuration as viewed along the bearing axis 26. The further sealing gap element 88 is of at least partially hollow cylindrical configuration. The further sealing gap element 88 has a central axis 90, wherein, in particular, the further sealing gap element 88 is arranged such that the central axis 90 of the further sealing gap element 88 is arranged within the bearing axis 26. The further sealing gap element 88 has an inner surface 92 and an outer surface 94 which are at least partially arranged at least substantially parallel to one another. The inner surface 92 and the outer surface 94 of the further sealing gap element 88 are at least partially arranged at least substantially parallel to the bearing axis 26. The further sealing gap element 88 has a side surface 96 which is arranged in particular transversely, preferably at least partially at least substantially perpendicularly, with respect to the bearing axis 26. The side surface 96 of the further sealing gap element 88 is delimited by the inner surface 92 and the outer surface 94 of the further sealing gap element 88. The further sealing gap element 88 is arranged on that wall 36 of the housing 12 which delimits the flow recess 38. The outer surface 94 of the further sealing gap element 88 is arranged at least predominantly on a side of the further sealing gap element 88 which is averted from the bearing axis 26. The inner surface 92 of the further sealing gap element 88 is arranged at least predominantly on a side of the further sealing gap element 88 which faces toward the bearing axis 26. In particular, as viewed at least substantially perpendicularly with respect to the bearing axis 26, the inner surface 92 of the further sealing gap element 88 is formed in a connecting region 98 of the further sealing gap element 88 and that wall 36 of the housing 12 which delimits the flow recess 38 and, preferably flush, in a plane with that wall 36 of the housing 12 which delimits the flow recess 38. The inner surface 92 of the sealing gap element 40 is preferably rounded, in particular oriented transversely with respect to the bearing axis 26, in the connecting region 98 of the further sealing gap element 88 and that wall 36 of the housing 12 which delimits the flow recess 38. The further sealing gap element 88 is configured and/or arranged such that the further sealing gap element 88, in particular the outer surface 94 of the further sealing gap element 88, at least partially delimits the spiral chamber 72. The further sealing gap element 88 is arranged between the impeller side chamber 28 and the spiral chamber 72. The further sealing gap element 88, in particular the side surface 96 of the further sealing gap element 88, at least partially delimits the fluid opening 76.

FIG. 2 shows the cross section of the turbomachine 10 in a region on one side of the drive axis 16 and/or of the bearing axis 26. The sealing gap element 40 has a maximum width 100 of in particular at most 5 mm, preferably at most 3 mm and particularly preferably at most 2 mm, which is in particular oriented at least substantially perpendicular to the bearing axis 26 and/or to the central axis 58 of the sealing gap element 40. The maximum width 100 of the sealing gap element 40 is in particular at least 1 mm, preferably at least 1.5 mm and particularly preferably at least 2 mm. The sealing gap surface 64 extends, as viewed at least substantially perpendicularly with respect to the bearing axis 26, at least substantially over the entire maximum width 100 of the sealing gap element 40. The conveying element 22 has, in particular at least substantially perpendicular to the drive axis 16, a maximum transverse extent 102 which is smaller than a minimum radial spacing 104 of the further sealing gap element 88, in particular of the inner surface 92 of the further sealing gap element 88, and the drive shaft 30. The maximum transverse extent 102 of the conveying element 22 is greater than a minimum radial spacing 106 of the sealing gap element 40, in particular of the inner surface 60 of the sealing gap element 40, and the drive shaft 30. The further sealing gap element 88 has a maximum width 108 of in particular at most 5 mm, preferably at most 3 mm and particularly preferably at most 2 mm, which is oriented in particular at least substantially perpendicular to the bearing axis 26 and/or to the central axis 90 of the further sealing gap element 88. In particular, the fluid opening 76 extends along the maximum width 108 of the further sealing gap element 88. The maximum width 108 of the further sealing gap element 88 is in particular at least 1 mm, preferably at least 1.5 mm and particularly preferably at least 2 mm. The further sealing gap element 88 has, in particular at least substantially parallel to the bearing axis 26, a greater maximum longitudinal extent than the sealing gap element 40.

As viewed at least substantially perpendicularly with respect to the bearing axis 26, the further sealing gap element 88 has a minimum radial spacing 110 to the bearing axis 26 which is greater than a minimum radial spacing 112 of the sealing gap element 40 and of the bearing axis 26, wherein the flow recess 38 is, as viewed from the bearing axis 26, arranged between the sealing gap element 40 and the further sealing gap element 88. The minimum radial spacings 110, 112 of the sealing gap element 40 and of the further sealing gap element 88 to the bearing axis 26 extend at least substantially perpendicular to the bearing axis 26. The minimum radial spacing 112 of the sealing gap element 40 extends from the inner surface 60 of the sealing gap element 40 to the bearing axis 26. The minimum radial spacing 110 of the further sealing gap element 88 extends from the inner surface 92 of the further sealing gap element 88 to the bearing axis 26. The minimum radial spacing 112 of the sealing gap element 40 is at least 40%, preferably at least 50% and particularly preferably at least 60% of the minimum radial spacing 110 of the further sealing gap element 88. The flow recess 38 is spanned within the impeller side chamber 28 by the sealing gap element 40 and the further sealing gap element 88 together with that wall 36 of the housing 12 which delimits the flow recess 38.

Two outer surfaces 92, 94, 96 of the further sealing gap element 88 which adjoin one another and which form a sealing edge 114 of the further sealing gap element 88, in particular the inner surface 92, the outer surface 94 and/or the side surface 96, span at least an angle 118 of less than 90°, preferably of less than 80° and particularly preferably of less than 70°, as viewed at least substantially perpendicularly with respect to the bearing axis 26, in particular in a vicinity of the sealing edge 114 of the further sealing gap element 88. The angle 118 that is spanned by the side surface 96 of the further sealing gap element 88 and the outer surface 94 or the inner surface 92 of the further sealing gap element 88, in particular in the vicinity of the sealing edge 114 of the further sealing gap element 88, is in particular less than 90°, preferably less than 80° and particularly preferably less than 70°. The sealing edge 114 of the further sealing gap element 88 is arranged at least substantially perpendicular to the bearing axis 26 and at least substantially all the way around the bearing axis 26. The sealing edge 114 of the further sealing gap element 88 is arranged such that at least one of two outer surfaces 92, 94, 96 of the further sealing gap element 88 which form the sealing edge 114 of the further sealing gap element 88, in particular the inner surface 92, is oriented at least substantially parallel to the bearing axis 26.

A maximum spacing 120, oriented at least substantially parallel to the drive axis 16, between the sealing gap element 40 and the conveying element 22 is in particular less than 2 mm, preferably less than 1.5 mm and particularly preferably less than 1 mm. It is preferable if the maximum spacing 120, oriented at least substantially parallel to the drive axis 16, between the sealing gap element 40 and the conveying element 22 extends from the sealing gap surface 64 of the sealing gap element 40 to the conveying element 22, in particular to at least one surface 122 of the conveying element 22 which is oriented at least substantially perpendicular to the drive axis 16. The sealing gap element 40 and the conveying element 22 are arranged such that a sealing gap is formed between the sealing gap element 40 and the conveying element 22, in particular by the maximum spacing 120. A maximum spacing 124, oriented at least substantially perpendicular to the drive axis 16, between the further sealing gap element 88 and the conveying element 22 is in particular less than 2 mm, preferably less than 1.5 mm and particularly preferably less than 1 mm. The maximum spacing 124, oriented at least substantially perpendicularly with respect to the drive axis 16, between the further sealing gap element 88 and the conveying element 22 preferably extends from the inner surface 92 of the further sealing gap element 88 to a side surface 126 of the conveying element 22 that borders the conveying outlet 46, wherein, in particular, the side surface 126 of the conveying element 22 is at least partially oriented at least substantially parallel to the drive axis 16. The further sealing gap element 88 and the conveying element 22 are arranged such that a further sealing gap is formed between the further sealing gap element 88 and the conveying element 22, in particular by the maximum spacing 124.

As viewed at least substantially perpendicularly with respect to the drive axis 16, the further sealing gap element 88 is arranged at least partially within a maximum longitudinal extent 128 of the conveying element 22. The maximum longitudinal extent 128 of the conveying element 22 is oriented at least substantially parallel to the drive axis 16. The further sealing gap element 88 is arranged, as viewed at least substantially perpendicularly with respect to the drive axis 16, outside a maximum longitudinal extent 130 of the conveying outlet 46 of the conveying channel 42, which is in particular oriented at least substantially parallel to the drive axis 16. The maximum longitudinal extent 130 of the conveying outlet 46 of the conveying channel 42 corresponds at least substantially to the opening width 78 of the fluid opening 76, which is in particular at least partially delimited by the further sealing gap element 88. In particular, the conveying element 22 is arranged relative to the separating device 20 such that the conveying outlet 46 and the fluid opening 76 are, as viewed in at least one section plane of the turbomachine 10 through the drive axis 16, arranged congruently one behind the other proceeding from the drive axis 16. As viewed in particular in at least one section plane of the turbomachine 10 through the drive axis 16, the side surface 96 of the further sealing gap element 88 is arranged at least partially in a plane with an inner surface 132, which delimits the conveying outlet 46, of the conveying element 22. The inner surface 132, which delimits the conveying outlet 46, of the conveying element 22 is oriented at least substantially perpendicular to the drive axis 16. The inner surface 132, which delimits the conveying outlet 46, of the conveying element 22 is arranged so as to be averted from the flow recess 38.

The conveying element 22 has a rounded portion 134 in an edge region on a side facing toward the sealing gap element 40 and/or the flow recess 38. It is alternatively or additionally conceivable for the conveying element 22 to have a bevel in the edge region on the side facing toward the sealing gap element 40 and/or the flow recess 38. The rounded portion 134 extends at least partially along the circumferential direction 56 around the drive axis 16. The rounded portion 134 is preferably arranged on the side surface 126 of the conveying element 22. The conveying element 22 has at least one sealing edge 136 which is in particular delimited by the side surface 126 and by the inner surface 132, which delimits the conveying outlet 46, of the conveying element 22. The sealing edge 136 of the conveying element 22 is at least partially configured so as to run at least substantially perpendicular to the drive axis 16 and along the circumferential direction 56 around the drive axis 16. The side surface 126 and the inner surface 132, which delimits the conveying outlet 46, of the conveying element 22 at least partially, in particular in a vicinity around the sealing edge 136 of the conveying element 22, have an angle 138 of in particular at most 90°, preferably at most 80° and particularly preferably at most 70°.

The sealing gap element 40 has the minimum spacing 112 to the drive axis 16 which corresponds to at most 90%, in particular at most 80%, preferably at most 70% and particularly preferably at most 60%, of a maximum radial extent 142 of the conveying element 22 around the drive axis 16. Preferably, the minimum spacing 112 of the sealing gap element 40 to the drive axis 16 corresponds in particular to at least 30%, preferably at least 40% and particularly preferably at least 50%, of the maximum radial extent 142 of the conveying element 22 around the drive axis 16. In particular, the minimum spacing 112 of the sealing gap element 40 to the drive axis 16 extends at least substantially perpendicular to the drive axis 16. The minimum spacing 112 of the sealing gap element 40 to the drive axis 16 preferably extends from the inner surface 60 of the sealing gap element 40 to the drive axis 16.

FIGS. 3 and 4 show an exemplary fluid and/or particle flow 34 through the turbomachine 10. FIG. 3 shows the turbomachine 10, analogously to FIG. 2 , in a cross section running through the bearing axis 26 and the drive axis 16. FIG. 4 shows the turbomachine 10 in a cross-sectional plane oriented at least substantially perpendicular to the bearing axis 26 and the drive axis 16. The conveying unit 18 is provided for moving the fluid and/or particle flow 34 through the conveying channel 42 into the impeller side chamber 28 and/or the spiral chamber 72. A fluid and/or particle flow 34 moving out of the spiral chamber 72 and/or the conveying channel 42 into the flow recess 38 and a fluid and/or particle flow 34 moving out of the flow recess 38 into the spiral chamber 72 and/or the conveying channel 42 are dependent on a volume, in particular on a cross-sectional area of the spiral chamber 72 at a position around the bearing axis 26. The spiral chamber 72 preferably has the at least substantially constant maximum longitudinal extent 80 along the circumferential direction 56 around the bearing axis 26, wherein, in particular, a maximum transverse extent 148 of the spiral chamber 72, which is oriented at least substantially perpendicular to the bearing axis 26, varies along the circumferential direction 56 around the bearing axis 26. If the maximum transverse extent 148 of the spiral chamber 72 is greater than a threshold value 150 of the maximum transverse extent 148 (cf. FIG. 4 ), the fluid and/or particle flow 34 moves out of the flow recess 38 into the spiral chamber 72 and/or the conveying channel 42. If the maximum transverse extent 148 of the spiral chamber 72 is smaller than the threshold value 150 of the maximum transverse extent 148 (cf. FIG. 4 ), the fluid and/or particle flow 34 moves out of the spiral chamber 72 and/or the conveying channel 42 into the flow recess 38. The separating device 20 is preferably provided for moving the fluid and/or particle flow 34 out of the spiral chamber 72 through the outlet opening 74 out of the turbomachine 10. 

1. A separating device for a turbomachine, the separating device having at least one housing (12) which has at least one bearing receptacle (24) defining at least one bearing axis (26) and which has at least one impeller side chamber (28), and the separating device having at least one swirling unit (32) for diverting and/or swirling at least one fluid and/or particle flow (34), wherein the swirling unit (32) has at least one flow recess (38), which is delimited by a wall (36) of the housing (12) and which extends within the impeller side chamber (28) so as to be spaced apart from the bearing axis (26), characterized in that the swirling unit (32) comprises at least one sealing gap element (40) which is arranged on a wall (36) of the housing (12) and which is configured for diverting and/or swirling at least one fluid and/or particle flow (34) flowing through the flow recess (38) along the bearing axis (26) and/or toward the bearing axis (26).
 2. The separating device as claimed in claim 1, characterized in that the sealing gap element (40) at least partially delimits the flow recess (38).
 3. The separating device as claimed in claim 1, characterized in that the swirling unit (32) comprises at least one further sealing gap element (88) which is arranged on a wall (36) of the housing (12) and which at least partially delimits the flow recess (38).
 4. The separating device as claimed in claim 1, characterized in that the swirling unit (32) comprises at least one further sealing gap element (88) which, as viewed at least substantially perpendicularly with respect to the bearing axis (26), has a minimum radial spacing (110) to the bearing axis (26) which is greater than a minimum radial spacing (112) of the sealing gap element (40) and of the bearing axis (26), wherein the flow recess (38) is, as viewed from the bearing axis (26), arranged between the sealing gap element (40) and the further sealing gap element (88).
 5. The separating device as claimed in claim 1, characterized in that the swirling unit (32) comprises at least one further sealing gap element (88), wherein at least two outer surfaces (92, 94, 96), which adjoin one another and which form a sealing edge (114), of the further sealing gap element (88) span an angle (118) of less than 90° as viewed at least substantially perpendicularly with respect to the bearing axis (26).
 6. The separating device as claimed in claim 1, characterized in that the swirling unit (32) comprises at least one further sealing gap element (88) which has a sealing edge (114) arranged such that at least one of two outer surfaces (92, 96), which form a sealing edge (114), of the further sealing gap element (88) is oriented at least substantially parallel to the bearing axis (26).
 7. A turbomachine, comprising at least one drive unit (14) which has at least one drive axis (16), at least one conveying unit (18) which is driven around the drive axis (16), which serves for conveying a fluid and which has at least one conveying element (22), and at least one separating device (20) having at least one housing (12) which has at least one bearing receptacle (24) defining at least one bearing axis (26) and which has at least one impeller side chamber (28), and the separating device having at least one swirling unit (32) for diverting and/or swirling at least one fluid and/or particle flow (34), wherein the swirling unit (32) has at least one flow recess (38), which is delimited by a wall (36) of the housing (12) and which extends within the impeller side chamber (28) so as to be spaced apart from the bearing axis (26), characterized in that the swirling unit (32) comprises at least one sealing gap element (40) which is arranged on a wall (36) of the housing (12) and which is configured for diverting and/or swirling at least one fluid and/or particle flow (34) flowing through the flow recess (38) along the bearing axis (26) and/or toward the bearing axis (26), wherein the conveying unit (18) is arranged at least predominantly within the impeller side chamber (28) around the drive axis (16).
 8. The turbomachine as claimed in claim 7, characterized in that a maximum spacing (120), oriented at least substantially parallel to the drive axis (16), between the sealing gap element (40) and the conveying element (22) is less than 2 mm.
 9. The turbomachine as claimed in claim 7, characterized in that the swirling unit (32) has at least one further sealing gap element (88) which, as viewed at least substantially perpendicularly with respect to the drive axis (16), is arranged at least partially within a maximum longitudinal extent (102) of the conveying element (22).
 10. The turbomachine as claimed in claim 9, characterized in that a maximum spacing (124), oriented at least substantially perpendicular to the drive axis (16), between the further sealing gap element (88) and the conveying element (22) is less than 2 mm.
 11. The turbomachine as claimed in claim 7, characterized in that the conveying element (22) has at least one bevel and/or at least one rounded portion (134) in an edge region on at least a side facing toward the sealing gap element (40) and/or the flow recess (38).
 12. The turbomachine as claimed in claim 7, characterized in that the sealing gap element (40) has a minimum radial spacing (112) to the drive axis (16) which corresponds to at most 90% of a maximum radial extent (142) of the conveying element (22) around the drive axis (16).
 13. The separating device as claimed in claim 1, wherein the swirling unit (32) is arranged on the housing (12).
 14. A coolant pump comprising at least one drive unit (14) which has at least one drive axis (16), at least one conveying unit (18), which is an impeller disk, which is driven around the drive axis (16), which serves for conveying a coolant, and which has at least one conveying element (22), wherein the conveying element is a vane, and at least one separating device (20) having at least one housing (12) which has at least one bearing receptacle (24) defining at least one bearing axis (26) and which has at least one impeller side chamber (28), and the separating device having at least one swirling unit (32) for diverting and/or swirling at least one fluid and/or particle flow (34), wherein the swirling unit (32) has at least one flow recess (38), which is delimited by a wall (36) of the housing (12) and which extends within the impeller side chamber (28) so as to be spaced apart from the bearing axis (26), characterized in that the swirling unit (32) comprises at least one sealing gap element (40) which is arranged on a wall (36) of the housing (12) and which is configured for diverting and/or swirling at least one fluid and/or particle flow (34) flowing through the flow recess (38) along the bearing axis (26) and/or toward the bearing axis (26), wherein the conveying unit (18) is arranged at least predominantly within the impeller side chamber (28) around the drive axis (16).
 15. The turbomachine as claimed in claim 14, characterized in that a maximum spacing (120), oriented at least substantially parallel to the drive axis (16), between the sealing gap element (40) and the conveying element (22) is less than 2 mm.
 16. The turbomachine as claimed in claim 15, characterized in that the swirling unit (32) has at least one further sealing gap element (88) which, as viewed at least substantially perpendicularly with respect to the drive axis (16), is arranged at least partially within a maximum longitudinal extent (102) of the conveying element (22).
 17. The turbomachine as claimed in claim 16, characterized in that a maximum spacing (124), oriented at least substantially perpendicular to the drive axis (16), between the further sealing gap element (88) and the conveying element (22) is less than 2 mm.
 18. The turbomachine as claimed in claim 17, characterized in that the conveying element (22) has at least one bevel and/or at least one rounded portion (134) in an edge region on at least a side facing toward the sealing gap element (40) and/or the flow recess (38).
 19. The turbomachine as claimed in claim 18, characterized in that the sealing gap element (40) has a minimum radial spacing (112) to the drive axis (16) which corresponds to at most 90% of a maximum radial extent (142) of the conveying element (22) around the drive axis (16). 